Control for presses



l0 Sheets-Sheet 1 Filed Dec. ll, 1945 [NV ENTOR v )4 rm/P/vzxs I July 3, 1951 'r. MAY 2,559,195

CONTROL FOR PRESSES I I Filed Dec. 11, 1945 10 Sheets-Shet 2 INVENTOR. M Q wtluu 1W /4 g; v

July 3, 1951 T. L. MAY

CONTROL FOR PRESSES l0 Sheets-Sheet 3 Filed Dec. 11, 1945 n J INVENTOR. v

July 3, 1951 T. 1.. MAY

CONTROL FOR PRESSES 10 Sheets-Sheet 4 Filed Dec. 11, 1945 INVENTOR.

ATTO/P/VEYS.

July 3, 1951 T. L. MAY 2,559,195

CONTROL FOR PRESSES Filed Dec. 11, 1945 10 Sheets-Sheet 5 6 INVENTOR.

W ill /w July 3, 1951 T. L. MAY

CONTROL FOR PRESSES l0 Sheets-Sheet 6 Filed Dec. 11, 1945 ATTOP/VV S July 3, 1951 MAY 2,559,195

CONTROL FOR PRESSES Filed Dec. 11, 1945 10 Sheets-Sheet 7 777' I, E? at y 3, 1951 T. L. MAY

CONTROL- FOR PRESSES l0 Sheets-Sheet 8 Filed Dec. 11, 1945 INVENTOR. 7/ 10/7/45 4557459 MAY July 3, 1951 11 MAY CONTROL FOR PRESSES l0 Sheets-Sheet 9 Filed Dec. 11, 1945 INVENTOR. Tim/7,45 455726,? May ATTOR/Vf r5 July 3, 1951 T. 1.. MAY 1 2,559,195

CONTROL FOR PRESSES Filed Dec. 11, 1945 10 Sheets-Sheet 1o INVENTOR. THO/7,45 55740? /'7/7 A TTO/P/V' VS Patented July 3, 1951 CONTROL FOR PRESSES Thomas Lestler May, New York, N. Y., assignor to Reliance Hydraulic Press, Inc., New York, N. Y., a corporation of New York Application December 11, 1945, Serial No. 634,155

9 Claims. 1

This invention relates to flywheel type punch presses.

An object of this invention is a flywheel punch press which is reliable in operation, can be operated at high speed, is silent in operation, has a long, efficient life and is of simple construction.

In a flywheel punch press embodying this invention, hydraulic means are provided for clutching and declutching the flywheel and crank shaft and additional hydraulic means are provided for applying and releasing brake means for the crank shaft. Cams rotatable with the crank shaft actuate four-way fluid valves to control the flow of hydraulic fluid to and from both bydraulic means. By reason of this structure, the noisy clicking incidental to mechanical clutch and brake-operating means is avoided, thereby rendering silent the operation of the press Means also are provided for preventing opera tion of the hydraulic means to clutch the flywheel and crank shaft except when the opera tors both hands are in a position of safety. Also, the press frame is mounted on a base for limited tilting movement whereby the angularity of the frame may be varied.

Other objects, novel features and advantages of this invention will become apparent from the following specification and accompanying drawings, wherein:

Fig. 1 is a front elevation of a press constructed in accordance with the invention;

Fig. 2 is a side elevation;

Fig. 3 is a section on the line 33 of Fig. 2;

Fig. 4 is a fragmentary end view of Fig. 3;

Fig. 5 is a section on the line 55 of Fig. 3;

Fig. 6 is a section substantially on the line 8-4: of Fig. 3;

Fig. 7 is a side elevation of Fig. 6;

Fig. 8 is a hydraulic diagram;

Fig. 9 is a fragmentary section generally similar to Fig. 3 of a modified embodiment of the invention;

Fig. 10 is a section on the line l0-Hl of Fig. 9;

Fig. ll is an elevation partially broken away of Fi 9;

Fig. 12 is an elevation generally similar to Fig. 11 of a further modification, and

Fig. 13 is a section on the line l3 l3 of Fig. 12.

A base H] has a frame ll pivotally connected thereto by means of a shaft l2. A hollow member I3 is pivotally supported at one end by the pin I mounted in the base In and in its free end the member I3 receives a rotatable member l5 havment 4| is attached to the hub 39 by bolts 42 and l ing a plurality of radial recesses Hi. The members 13 and 15 are provided with cooperating shoulders to limit movement of the member I5 toward the pivot pin l4 and the member I5 is provided with a peripheral groove I'I into which projects the inner end of a screw l8 mounted in the member l3 to prevent withdrawal of the member !5 from the member IS. The member I5 has a threaded bore in which is arranged a lag screw N3, the upper end of which has a transverse bore through which passes a pin H], the ends of which are arranged in ears formed on the frame H. The shaft I2 is located near the front of the base and the lag screw iii, in combination with its asso-- ciated parts, provides means for tilting the frame H at any desired angle upon rotation of the member 55 through the medium of a bar inserted in the recesses H5. The frame II carries a pin 2! projecting through an arcuate slot in the base it concentric with the pivot pin 12 and serves serves to limit the extent of tilting of the frame I! as well as to indicate the extent of tilting by reason of indicia provided in suitable relationship to the slot 22 for that purpose.

A crank shaft 23 is journalled in the frame II and a pitman rod 24 is attached in the usual manner to the crank pin 25 of the crank shaft 23. The lower end of the pitman rod is attached. in the usual manner to a head 26 slidably supported by vertical guides 21 for movement toward and away from the bed 28 in the usual manner. lhe frame H supports a motor 2S and an oil pump 30 which is driven by the motor through the medium of a belt 3|.

A flywheel 32 is journalled on one end of the crank shaft 23 and is driven by the motor 29 through the medium of a belt 33. A thrust bear ing 34 is interposed between one face of the flywheel 32 and a shoulder 35 on the crank shaft 23. A circular clutch element 36 is held against the outer face of the flywheel 32 by bolts 3"! and is provided with an inner tapering surface it. A hub 39 is supported by the crank shaft 23 and is keyed thereto by a spline 48 so that the hub and shaft rotate in unison and the hub is mov-- able axially of the shaft. A circular clutch elehas an outer conical face 43 complementary to the face 38 of the clutch element 36. A strip i of standard clutch facing material is fixed to the clutch element 4| and is arranged between the surfaces 43 and 38.

The extreme end of the crank shaft 23 has a threaded portion 45 of reduced diameter and a circular piston 46 has an interiorly threaded bore co-operating with the threaded portion 35 to attach the piston to the end of the shaft. A block. 41 has a cylindrical bore 51a of two different diameters with the smaller diameter portion receiving the crank shaft and the larger diameter portion receiving the piston 45. The block 41 is attached to the collar 39 by bolts 48. A head 53 fits the outer end of the block 91 and has an extension 59. A passageway leads from the in ner end of the cylinder to a radial port 52 in the extension 50 while a passageway 53 leads from the outer end of the cylinder through the extension to a radial port 54. The cylinder lia and the piston 45 constitute a hydraulic motor for ac tuating the clutch element 4| by reciprocation of the block 61 on the crank shaft 23. A cap is journalled on the extension 59 and has circular recesses 56 and 51 communicating respec tively with the ports 52 and 54. Ports 5B and in the sleeve communicate with the recesses 55 and 51 respectively.

A brake drum 5|? is fixed to the remaining end of the crank shaft 23 by a key 5|. A split brake band 62 is supported by the frame l I through the medium of a post 63 and is provided with a suitable brake lining 63a. The two sections of the brake band are urged toward the drum 62 by a spring 54 arranged on a rod 65 extending through the free ends of both of the band sections and having nuts 65 and 61 at the opposite ends thereof with the spring 64 arranged between one band section and the nut 61 which is adjustable to vary the tension exerted by the spring 64. A roller 68 is carried by a yoke at the end of the piston 69 of a hydraulic motor 19. The roller 68 is adapted to be projected by the hydraulic motor between the ends of the brake sections for the purpose of stretching apart the band sections to release the crank shaft. Upon withdrawal of the roller 58, the spring 65 urges the band section into engagement with the brake drum 69 to oppose rotation of the shaft 23.

A sleeve 1| is keyed to the crank shaft 23 and is provided with a pair of cams l2 and 13 which have high sections 1241 and 1311 respectively and low sections 12b and 13b respectively. Cam followers 14 and for co-operation with the peripheries of the cams 12 and 13 respectively are arranged at the ends of levers 15 and 11 respective- 1y, fulcrumed on a common pivot pin 18. A pair of standard four-way fluid valves 19 and 89 are suitably arranged below the free ends of the levers 16 and 11 respectively for actuation thereby. The valves 19 and 89 have actuating plungers 19a and 80a respectively, as well as springs 19b and 8922 respectively for normally maintaining the plunger in a predetermined adjustment. The plunger 19a and 89a are located respectively in the paths of the ends of the levers 15 and 11 opposite the cam followers 14 and 15. A rod 8| slidably carries a cross-bar 82 engaging the upper surface of the levers 16 and 11 on the opposite side of the pivot pin 18 from the cam followers. A spring 83 is interposed between the cross bar and a nut 85 on the end of the rod. The rod 8| is mounted in guides 85 and at its lower end is connected to the upper end of link 86, the lower end of which is connected to one arm of a bell crank lever 81, the other end of which is connected by a cable 88 passing over suitable guide rollers 89 and 99 to a foot pedal 9|. The arrangement is such that upon depression of the pedal 9|, the rod 8| is caused to move downwardly.

An oil supply pipe 92 leads from a pump to the inlet port of the four-way valve 19 and a pipe 92a leads from the return port of said valve to a reservoir (not shown). A pipe 93 leads from the third port of the valve 9| to the port 58 of the cap 55 while a pipe 94 leads from the fourth port of the valve 19 to the port 59 of the cap 55. Similar connections 95, 95a, 96 and 91 are provided between the pump 39 and the four-way valve 80 and between said valve and the hydraulic motor 10.

The arrangement is such that with the clutch inoperative and the brake operative, the cam followers 14 and 15 contact the low sections 1227 and 19b of the cams 12 and 13, as indicated in Figs. 4 and 5 near the trailing ends thereof. With the parts in the position shown in Figs. 4 and 5, the valve plungers 19a and 89a are in such position that hydraulic fluid is supplied under pressure to the upper end of the hydraulic motor 19 to locate the roller 98 out of engagement with the brake sections to permit the spring 64 to hold the brake sections against the drum 60 to oppose rotation of the crank shaft and hydraulic fluid is supplied under pressure to the outer ends of the cylinder 41a to hold it and the drum 4| with the clutch facing '46 out of engagement with the.

member 36 so that the flywheel 32 rotates freely on the shaft 23. The pedal 9| is in its uppermost position to which position it is biased by the springs 19b and 89b. Upon depression of the pedal 9|, the levers 19 and 11 are tilted to lift the cam followers 14 and 15 and to depress both valve plungers 19a and 89a whereupon the supply of hydraulic fluid to the motor 10 is reversed to force the roller 68 between the ends of the brake sections to release the crank shaft 23 for rotation. Also, the supply of hydraulic fluid to the cylinder 41 is reversed to apply pressure urgin the cylinder 41 in the direction to engage the clutch facing 44 with the surface 38 to clutch the flywheel to the crank shaft to cause rotation of the latter. The cams 12 and 13 rotate counterclockwise from the position shown in Fig. 4 to locate the high sections 12a and 13a. under the cam followers to hold the levers 16 and 11 tilted after the release of the pedal 9|. After predetermined extent of rotation of the crank shaft, the cam followers ride off the high sections 12a and 13a into contact with the low sections 121) and 1312 thereby permitting return of the fourway valves 19 and 80 to their original positions under the influence of their springs and corresponding return of the levers 16 and 19 to original position. The extent of the high section 13a is greater than the extent of the high section 12a so that the clutch is released before the brake is actuated. The hydraulic motor 19 is thereupon actuated to withdraw the roller 68 from between the ends of the brake band sections and also the clutch hydraulic motor is actuated to disengage the clutch facing 44 from the surface 38 thereby stopping the crank shaft after one complete revolution.

Declutching of the flywheel from the crank shaft is facilitated by springs 91 seated in sockets in the hub 39 and bearing against a collar 98 attached to the crank shaft 23 and engaging the flywheel 32. A suitable packing 99 provides a fluid-tight seal between the crank shaft 23 and the block 41. The end of the cap 55 is formed as a detachable cover I00 and a plate l-fll 'attached to the end of the shaft 23 by'bolts-"IB2 holds the cap in position on the shaft: against a shoulder I93. At each end of the-cap 5 5'there is provided a circular chamber I94 connecting with a longitudinal chamber I05 arranged below the extension 50. The cover I09 closes one chamber I04 while a sealing member I06 closes the other. Any hydraulic fluid which escapes along the surface of the extension 50 from the grooves 52 and 54 is conducted by the chambers I04 to high and low sections 12a and 13a respectively.

This construction will be described only in connection with cam I2 but it is to be understood that the cam 13 is of the same construction. The cam I2 is provided with a low section 12a of definite length and the cam supports an arcuate member I08 by studs I09 passing through arcuate slots H in the cam 52 coaxial therewith. The member I09 is provided with high and low sections I98a and I081) corresponding to the high and low sections 12b and 13b. By rotatable adjustment of the member I08 the effective lengths of the high and low sections of the cam may be varied within limits thereby varying the timing of the valve I9.

The press is equipped with mechanism to prevent operation of it except when the operators hands are both in positions of safety. A bleed II'I leads from the pipe 94 through which the hydraulic fluid is supplied to the clutch-operating hydraulic motor for the purpose of clutching the shaft 23 to the flywheel 32. The bleed III is controlled by a valve I I2 operated by a solenoid II3, the arrangement being such that with the solenoid deenergized, the valve is opened allowing hydraulic fluid to pass through the bleed from the pipe 94 to a reservoir (not shown). The energizing circuit for the solenoid includes a pair of palm switches H4 and II arranged in front of the press bed 28 (Fig. 1) These switches are self-opening and are closed by downward pressure of the operators hands and both switches must be closed in order to energize the solenoid H3. Should the pedal 9I be tripped with either switch H4 and II5 open, the pressure of the hydraulic fluid supplied to the clutchoperating motor will be insufficient to energize it because of the fact that the bleed III is open and hydraulic fluid is by-passed therethrough to the reservoir. In order to clutch the flywheel 3-2 to the shaft 23, both switches H4 and H5 must be closed and the pedal 9I depressed.

In Figs. 9 to 11 inclusive, the frame II supports a casing I25 having an aperture through which the shaft 23 extends. The brake drum 60 is enclosed by a brake band I29, one end of which is attached to one end of a rod I27 and the other end of which is attached to the short arm of a bell crank lever I28 supported by a pivot pin I29. The brake drum 60 supports two cams I30 and I3I which are adjustably mounted on the brake drum 60 by bolts I32 extending through arcuate slots I33. The end of the long arm of the bell crank lever I28 is pivotally connected to the piston 69 of the hydraulic motor Ill. The rod I27 passes through an eye I28a in the long arm of the bell crank lever I28 and has its remaining end threaded to receive a sleeve I34 engaging said bell crank lever arm to cause downward movement of the rod I2! upon counterclockwise rotation of the bell crank lever I28.

The four-way valve I9 controls the flow of hydraulic fluid to and from the brake motor I0 as well as the clutch motor and the valve 80 is dispensed with. The pipe 92 supplies hydraulic fluid to the valve I9 from the pump and hydraulic fluid is discharged from the valve 19 through the pipe 92a to the reservoir. The pipes 93 and 96 communicate with one port of the valve I9 while the pipes 94 and 91 communicate with a second port of the valve I9.

An arm I35 is pivotally supported from the frame II by the pin I36 and is attached to the link 85 by a pin I3I. Down-ward movement of the link 86 by operation of the treadle 9I causes clockwise rotation of the arm I35. A rocker I38 is supported from the frame II by a pivot pin I39 and at its right end is provided with a roller I40 for engagement with the cam I3I. At its left end, the rocker I38 carries an adjustable bolt I4I for engagement with the plunger 79a of the four-way valve I9. counterclockwise rotation of the rocker I38 causes downward movement of the plunger 19a of the valve I9 against the action of its spring 191).

The free end of the arm I35 pivotally supports an arm or bar I42 carrying a roller I43 and a spring I44 biases the arm I42 counterclockwise against a stop illustrated as being a pin I45 carried by the arm I35. The roller I43 engages a plate I45 carried by the rocker I38 at its left end. The arrangement is such that with the arm I42 engaging the pin I45 counterclockwise rotation of the lever I35 urges the lever I42 counter-clockwise against the stop.

The casing I25 supports a bracket having a pair of spaced arms I4I and I48 in which is slidably mounted a plunger I49 in alinement with the arm I42. Between a collar I50 on the plunger I49 and the arm I4! is provided an expansion spring I5| tending to maintain the collar I50 against the arm I48. The housing I25 has a slot I52 through whichextends a stud I53 projecting from a slide I54 engaging the slide I54 by a pin I59.

inner surface of the housing. A vertical arm I55 is pivotally attached at its lower end to the In the upper end of the arm I55 is a recess I51 receiving the right end of the plunger I49. An extension I58 from the arm I55 carries a cam follower I59 adapted for engagement with the cam I30. A hand-operable nut I60 is threaded onto the stud I53 for tightening against the outer surface of the easing I25 to maintain the slide I54 in any desired position along the slot I 52.

The hydraulic motor I9 is pivotally suspended at its upper end from a pin IGI carried by a bracket I62 forming part of the frame II. A threaded rod I63 is supported at one end by a pin I64 also carried by the bracket I62. The rod I63 projects through an eyelet I28b in the longer arm of the bell crank lever I28. A spring I55 carried by the rod I63 biases the bell crank lever I28 counterclockwise and serves to apply the brake in the event of failure of hydraulic pressure.

The frame II supports a double-acting hydraulic motor I66, the piston IBI of which is attached to a slide I68 supported in alinement with the cam I30 which is provided with a radial shoulder I 69 for engagement with the slide I88 in one position thereof. The upper end of the hydraulic motor I63 is connected by the pipe IIO through the same port of the four-way valve I9 as the pipe 93 while the lower end of the hydraulic motor I93 is connected through the pipe Ill with the same port of the valve I9 as the pipe 94. With the piston I61 in its lower position, the slide I68 extends into the path of the shoulder I69 while with the piston I 61 in its upper position the slide is out of the path of the shoulder I69.

The cam I3I has a high section I3 Ia and a low section I3Ib which co-operate with the cam follower I40 in the same manner as the sections 120. and 12b of the cam 12 co-operate with the cam follower 14 of the embodiment of Figs. 1 to 8 inclusive. The cam I has a short section I30a of greater radius than the remainder, which section is approximately opposite the shoulder I69 and is adapted to engage the roller I59 in one setting of the slide I54. With the shaft 23 at rest, the follower I40 contacts the low cam section I3Ib near the trailing end thereof and the section I30a. is oriented from the roller I59 approximately 90.

The apparatus just described may be arranged to operate continuously as long as the pedal 9I is actuated or to stop at the end of one complete rotation of the shaft 23 irrespective of whether or not the pedal is released. The single rotation operation will be first described. With the pedal 9I released, the plunger 19a of the four-way valve 19 is in its uppermost position and the valve 19 is so set that hydraulic fluid is supplied to the clutch motor to release the shaft 23 from the flywheel 32 and that hydraulic fluid is supplied to the motor 10 to maintain the plunger 69 in its lowermost position with the brake applied and that hydraulic fluid is supplied to the motor I66 to locate the slide I68 in the path of the shoulder I69. The cam follower I40 contacts the low section 'I3Ib of the cam I3I near the trailing end thereof and the rocker I38 is in its extreme clockwise position. The slide I54 is at its extreme right position with the follower I59 in position to be engaged by the section I36a. of the cam I30.

Upon operation of the treadle 9|, the link 86 moves downwardly to rotate the arm I clockwise and through the intermediary of the arm I42, roller I43 and plate I46 rotates the rocker I38 counter-clockwise to depress the plunger 19a. and change the setting of the valve 19 and lift the follower I40 away from the low cam section I3Ia. With the new setting of the valve 19, the flow of hydraulic fluid to the clutch, brake and latch motors is reversed so that the brake is released, the clutch is actuated and the slide I68 is lifted out of the path of the shoulder I69. Initial rotation of the shaft 23 locates the high portion I3Ia of the cam I3I under the follower I40 to prevent clockwise rotation of the rocker I36 and maintain engagement of the roller I43 with the plate I46. Continued rotation of the shaft 23 brings the high spot I30a. of the cam I30 into engagement with the roller I59, thereby causing counter-clockwise rotation of the arm I and movement of the plunger I48 to the left to swing the arm I42 past its dead-center position, thereby freeing the rocker I38 for clockwise movement under the influence of the return spring 19b for the plunger 19a. Upon further rotation of the shaft 23, the high section I3Ia moves out of engagement with the follower I49, thereby permitting return of the rocker I38 as well as the valve plunger 19a to original position. Upon return of the valve 19 to its original setting, the clutch is released, the brake applied and the slide I 61 projected into the path of the shoulder I68. After release of the treadle 9|, the arm I35 rotates counterclockwise to its original position, thereby permitting return of the arm I42 to-the position shown in Fig. 12 under the influence of the spring I44.

For continuous operation, the slide I54 is moved to the left a sufiicient distance-that the roller I59 is not engageable by the high section I30a of the cam I36. The plunger I48, therefore, is not operated and the arm I42 remains in position to keep the rocker I38 fully rotated counter-clockwise and the plunger 19a. in its lowermost position until such time as the lever I35 is returned to its original position by release of the treadle 9|.

The modification of Figs. 12 and 13 is fundamentally similar to that of Figs. 9 to 12 inclusive but differs in respect of certain structural details which will hereinafter be described.

The brake band I26 is attached at one end to a fixed pin I12 and is provided at its opposite end with a sleeve I13 in which is slidably mounted a rod I14. A-spring I15 is interposed between the sleeve I13 and a nut I16 on the rod I14 to the right of the sleeve. The left end of the rod I14 is pivotally connected to one extremity of a lever I11 pivotally supported on a pin I18. A link I19 is pivotally connected at one end to the remaining end of the lever I11 and its other end is pivotally connected to the piston 69 of the hydraulic motor 10 by a pin I80. An arm I8I is pivotally supported at one end by a fixed pin I82 and its remaining end is pivotally connected to the piston 69 by the pin I89. The arm I6I and link I19 constitute a toggle which, when in the straight position, as shown in Fig. 12, clamps the brake band 525 around the brake drum 60 with the piston 69 in its lowermost position. Upward movement of the piston 69 breaks the toggle and effects clockwise movement of the lever I11 to move the rod I14 to the right, thereby releasing the brake.

The arm I55 is pivotally connected at its lower end by a pin I83 to one end of a lever I84 pivoted on the pin I85. Stop pins I86 and I81 limit the swinging movement of the lever I84. With the lever I84 engaging the pin I86, the arm I55 is in position-to have the cam follower I59 engaged by the high spot I30a of the cam I30 while with the lever I84 engaging the stop I81, the arm I55 is in such position that the roller I59 is out of the path of the high spot I30a. A pin I88 engages the right side of the arm I55 near its upper end to retain it in proper position.

A bell crank lever I89 is pivotally supported on the pin I90 and one arm of the bell crank lever has a portion I9I adapted for movement into the path of the shoulder I 69. The remaining arm of the bell crank lever is pivotally connected by a pin I92 to the piston I 61 of the hydraulic motor I66. With the piston I 61 in its extreme right position, the portion I9I is in the path of the shoulder I69 while in the extreme left position of the piston I61 the part I9I is out of the path of the shoulder I69.

A pipe I93 leads from one port of the four-way valve 19 to a T I94 from which the pipe 96 leads to the lower end of the motor 10 and the pipe I95 leads to the right end of the motor I66. A port I96 in the motor I66 is connected through pipe I91 to a T I98, one arm of which connects to the pipe 94 leading to the clutch motor. The other arm of the T I98 communicates with the inlet of a check valve I99, the outlet of which communicates with the pipe I95. The remaining port of the valve 19 communicates through a pipe 200 with a T 20I, one arm of which communicates with the upper end of the motor 16 through the pipe 91 and the other arm communicates through the pipe 93 with the left end of the clutch motor. The motor 10 has a port 202 which communicates with a pipe 203 leading to a T 204, one arm of which communicates through the pipe 205 with the left end of the motor I66. The remaining arm of the T 204 communicates with the inlet of a check valve 206, the outlet of which communicates with said T 20I. The port I96 is so arranged in the motor I66 that it is covered by the piston I-6'I except when the piston is at the left end of its path. The port 202 in the motor I is so arranged that it is covered by the piston 69 except when the piston is at the lower end of its stroke.

With the elements in the position shown in Fig. 12, the valve I9 is so set that hydraulic fluid pressure is applied to the upper end of the motor and to the left end of the motor I66 and to the right end of the clutch motor so that'the clutch is out, the latch is in and the brake is on. Upon operation of the treadle 9|, the setting of the valve I9 is reversed whereupon hydraulic fluid flows through the pipe 96 into the bottom of the motor 10 to lift the piston 69 and release the brake and through the pipe I95 into the right end of the motor I66 to move the piston I61 to the left, thereby releasing the latch Isl. After the latch has been released, hydraulic fluid flows from the motor its through the pipe I91 and pipe 94 to the left end of the clutch motor to throw in the clutch. Hydraulic fluid flows from the right end of the clutch motor through the pipe 93 to the valve I9, from the cylinder 1 through the pipes 91 and 200 .to the valve I9 and from the motor I66 through the pipe 25 and check valve 206, to the valve 19. After a single rotation of the shaft 23, the valve I9 is returned to its original position by operation of the arm I55, plunger I48 and arm I42 as described in connection with the previous modification. Hydraulic fluid then flows from the valve 19 through the pipes 200 and 91 to the upper end of the motor I0 to force the motor piston downward into brake-applying position. When the motor piston reaches such position, hydraulic fluid then flows through the pipe 203 to the elbow 204 and through the pipe 205 to the left end of the motor I66. Hydraulic fluid also flows through pipe 93 to the right end of the clutch motor. Hydraulic fluid flows from the bottom of the motor I0 through the pipes 96 and I93 to the valve I9, from the right end of the motor I66 through the pipe I95 to the valve I9 and from the right end clutch motor through the pipe 93, the check valve I99 and pip-e I95 to the valve I9. The check valve I99 provides a bypass for hydraulic fluid from the clutch motor around the motor I66 in its flow to the valve I9 during the release of the clutch. The check valve 296 provides a by-pass around the motor I0 for hydraulic fluid flowing from the motor I66 to the valve 19 when the piston of the motor '10 is in its brake-released position.

A bracket 201 is pivotally supported by the bell crank lever I89 and has an aperture through which slidably extends a rod 28, one end of which i pivotally connected to the brake band I26. At the other end of the rod 208 is provided an adjustable abutment between which and a portion of the bracket is arranged an expansion spring 209 surroundig the rod 28. Upon release of the brake mechanism and disengagement of the bell crank lever from the shoulder I69, the spring 209 tends to lift the brake band I26 away from the brake drum 60.

It is to be understood that various modifications may be made in the device above described without in any way departing from the spirit of the invention a defined in the appended claims.

This application is a continuation-in-part of applicants co-pending application, Serial No. 570,621, filed December 30, 1944, now Patent Number 2,493,495, issued January 3, 1950.

I claim:

1. In a punch press having a crankshaft, a pivoted arm, a manually actuated pivoted rocker, interengaging means on said arm and rocker for effecting rotation of said rocker upon rotation of said arm, a rotatable cam connected with said crankshaft, and means actuated by said cam for rendering inoperative said interengaging means to permit limited rotation of said rocker independent of said arm.

2. In a punch press, a pivoted arm, a pivoted rocker, interengaging means on said arm and rocker for effecting rotation of said rocker upon rotation of said arm, a rotatable cam, an adjustably supported cam follower, and means actuated by said cam follower for rendering inoperative said interengaging means to permit limited rotation of said rocker independent of said arm.

3. A punch press comprising a rotatable crank shaft, a hydraulic system including a valve for controlling rotation of said crank shaft, means including a rocker for actuating said valve, a pivoted arm, interengaging means on said arm and rocker for effecting rotation of said rocker upon rotation of said arm, a cam rotatable with said shaft, and means actuated by said cam for rendering inoperative said interengaging means to permit limited rotation of said rocker independent of said arm.

4. A punch press comprising a rotatable crank shaft, a hydraulic system including a valve for controlling rotation of said crank shaft, means including a rocker for actuating said valve, a pivoted arm, interengaging means on said arm and rocker for eifecting rotation of said rocker upon rotation of said arm, a cam rotatable with said shaft, an adjustably supported cam follower, and means actuated by said cam follower for rendering inoperative said interengaging means to permit limited rotation of said rocker independent of said arm.

5. A punch press comprising a rotatable crank shaft, a hydraulic system including a valve for controlling rotation of said shaft, means including a rocker arm for actuating said valve, a pivoted arm, means including a pivoted element supported by one arm for engagement with the other arm to effect rotation of said rocker arm upon rotation of said one arm, a cam rotatable with said shaft, and means actuated by said cam for swinging said element into position to permit limited rotation of said rocker independent of said arm.

6. A punch press comprising a rotatable crank shaft, a hydraulic system including a valve for controlling rotation of said shaft, means including a rocker arm for actuating said valve, a pivoted arm, means including a pivoted element supported by one arm for engagement with the other arm to effect rotation of said rocker arm upon rotation of said one arm, a cam rotatable with said shaft, an adjustably supported cam follower, and means actuated by said cam follower for swinging said element into a position to permit limited rotation of said rocker independent of said arm.

7. A punch press comprising a rotatable crank shaft, a hydraulic system including a valve for controlling rotation of said crank shaft, means including a rocker for actuating said valve, a pivoted arm, a bar pivoted at one end to said arm and having its other end engageable with one end of said rocker, a stop engageable by said bar in position to effect rotation of said rocker upon rotation of said arm, resilient means biasing said bar toward said stop, a plunger adapted to engage said bar to move it away from said stop, means biasing said plunger away from said bar, a cam rotatable with said crank shaft, and a movable member engaging said plunger, said cam having a raised portion engageable with said member to effect movement of said plunger into engagement with said bar to swing the latter into position to release said rocker.

8. A flywheel press including in combination a flywheel, a crankshaft, a clutch constructed and arranged to rotatively interconnect said flywheel and said crankshaft when said clutch is engaged, a reciprocative controller constructed and arranged to disengage said clutch when moved to a first position and to engage said clutch when moved to a second position, rotory cam means connected with said crankshaft to rotate therewith, a reciprocative cam follower connected with said controller to reciprocate the latter, said cam means having a rotary cam surface engaged by said follower with said surface having a low portion moving said follower to a first position moving said controller to said first position and a high portion moving said follower to a second position moving said controller to said second position and said follower being free to move away from said low portion to said second position and being biased to move towards said low portion, a manually controlled reciprocating operator moving between first and second positions, latch means constructed and arranged to latch said operator in connection with said follower when said operator and said follower are respectively at their said first positions and to remain latched during their movement respectively to their said second position and when released to relatch only when said operator and said follower arerespectively at their said first positions, a

reciprocative latch release engaging and releasing said latch when said release is moved in one direction, and a second reciprocating cam follower connected with said latch release to move it in said direction, said cam means including a rotary riser engaged by said second follower after said cam means starts to be rotated by said crankshaft when said manually controlled operator is initially moved from its said first position to its said second position.

9. A flywheel press including in combination a flWheel, a crankshaft, a clutch constructed and arranged to rotatively interconnect said flywheel and said crankshaft when said clutch is engaged, a reciprocative controller constructed and arranged to disengage said clutch when moved to a first position and to engage said clutch when moved to a second position, rotary cam means connected with said crankshaft to rotate therewith, a reciprocative cam follower connected with 12 said controller to reciprocate the latter, said cam means having a rotary cam surface engaged by said follower with said surface having a low portion moving said follower to a first position moving said controller to said first position and a high portion moving said follower to a second position moving said controller to 'said second position and said follower being free to move away from said low portion to said second position and being biased to move towards said low portion, a manually controlled reciprocating operator moving between first and second positions, latch means constructed and arranged to latch said operator in connection with said follower when said operator and said follower are respectively at their said first positions and toremain latched during their movement respectively to their said second position and when released to relatch only when said operator and said follower are respectively at their said first positions, a reciprocative latch release engaging and releasing said latch when said release is moved in one direction, and a second reciprocating cam follower connected with said latch release to move it in said direction, said cam means including a rotary riser engaged by said second follower after said cam means starts to be rotated by said crankshaft when said manually controlled operator is initially moved from its said first position to its said second position, said second follower being mounted for movement between a first position where it is engaged by said riser and a second position where it is freed therefrom and rendered inoperative.

' THOMAS LESTLER MAY.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 158,496 Jackson Jan. 5, 1875 304,479 Weston Se t-2, 1884 615,441 Emmerich et a1. D 6, 1898 975,589 Watkins Nov. 15', 1910 1,520,733 Turney Dec.-'3O,. 19 24 1,544,766 Leschhorn July-1219,25

1,547,355 Bayer et al. July 28, 1925 1,612,239 Turney Dec. 28, 1926 1,819,641 Davis Aug. 18, 1931 1,863,425 Wallbillich et a1. June 14, 1932 1,869,085 Williamson July 26, 1982 1,894,434 Williamson Jan. 17, 1983 2,068,062 Metten Jan. 19, 1937 2,085,040 Post ---r'---r--.'-'-: ne 9 19. 7

2,192,734 Clouse Mar. 5, 1940 2,193,880 Peet Mar. '19, 1940 2,250,629 Freidman July 29, 19.41

2,295,161 Clay Sept. 8, 1942 2,308,679 Eason Jan. 19, 1943 2,357,779 Criley Sept. 5, 1944 2,452,775 Lindsley Nov. 2, 1 948 2,493,495 May Jan. 3, 1950 Certificate of Correction Patent No. 2,559,195 July 3, 1951 THOMAS LESTLER MAY It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows:

Column 1, line 19, after press insert a period; column 2, line 22, strike out serves, second occurrence; column 3, line 20, for the indistinct numeral after and, second occurrence, read 59; line 41, for section read sections; column 4:, line 24, for ends read end; column 5, line 36, for deenergized read ale-energized; column 11, line 23, for rotory read rota column 12, following line 46, list of references cited, insert the following:

978,776 Morgan Dec. 13, 1910 and that the'said Letters Patent should be read as corrected above, so that the same may conform to the record of the case in the Patent Oflice.

Signed and sealed this 25th day of September, A. D. 1951.

THOMAS F. MURPHY,

Assistant Commissioner of Patents. 

